US3830211A - Centrifugal governor for controlling the rpm of injection type internal combustion engines - Google Patents

Centrifugal governor for controlling the rpm of injection type internal combustion engines Download PDF

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Publication number
US3830211A
US3830211A US00362302A US36230273A US3830211A US 3830211 A US3830211 A US 3830211A US 00362302 A US00362302 A US 00362302A US 36230273 A US36230273 A US 36230273A US 3830211 A US3830211 A US 3830211A
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United States
Prior art keywords
lever
force
spring
improvement
control spring
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Expired - Lifetime
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US00362302A
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English (en)
Inventor
H Bechstein
E Ritter
H Staudt
H Jaenke
R Mueller
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/04—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by mechanical means dependent on engine speed, e.g. using centrifugal governors
    • F02D1/045—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by mechanical means dependent on engine speed, e.g. using centrifugal governors characterised by arrangement of springs or weights
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • F02D1/10—Transmission of control impulse to pump control, e.g. with power drive or power assistance mechanical

Definitions

  • the invention relates to a centrifugal governor for controlling the rpm of injection type internal combustion engines having a fuel injection pump, which governor has a housing and a regulator member being displaceable as a function of the rpm, and the regulating movements of which member are transmitted, by means of a two-armed cam lever having lever arms which are adjustable dependent upon the position given an externally turnable operating lever, to fuel delivery control means associated with the fuel injection pump, wherein the fuel delivery control means, upon completing a first part of its movements against the force of a first control spring, acts on a forcetransmitting lever which is biassed by at least one second control spring, and the force-transmitting lever bears an adjusting screw for setting the first control spring to a low rpm, and is adapted for swivelling about an axis
  • a disadvantage of the known governors resides in that the adjustment of the rpms to be regulated and the adjustment of the working ranges of the governor, i.e., the exact coordination of the respective positions of the fuel delivery control member in relation to the positions of the regulator member, is intricate, as some individual adjustment steps will influence, at least in part, others.
  • the adjustment of the full-load position of the regulator sleeve will cause changes in the initial tension of the no-load control spring as well as that of the fullload control spring.
  • a particularly advantageous feature of the rpmregulating governor according to the invention is provided by the fact that the force-transmitting lever, in its 7 neutral position, is disposed at least approximately perpendicular to the axis of the regulating member, and that the adjusting screw of the bearing lever, the adjusting member and the adjusting screw for the first control spring are screwed into the force-transmitting lever parallel in relation to one another and at least approximately parallel to the axis of the regulator member, and that they are secured in their position.
  • This at least approximately horizontal arrangement of all adjusting elements is especially advantageous, since it allows an adjustment of the governor with access only from the front end thereof.
  • a further advantage resides in that this arrangement facilitates the use of an automated adjusting device.
  • a stop screw isfitted into the governor housing in a position at least approximately parallel to the adjusting screws and to the adjusting member, which stop screw serves as a stop for the force-transmitting lever.
  • This stop screw also could be adjusted with advantage by means of an automated setting device.
  • the second control spring is devised as a tension spring which is arranged at least approximately in parallel to the force-transmitting lever, and the one end of which is connected to a bearing bolt which is rotatably mounted in the governor housing in parallel to the axis of the regulator member, and rotary displacement of which changes the effective direction of the second control spring and thereby causes an adjustment in the proportional range of the governor.
  • the force-transmitting lever features an essentially U- or H-shaped cross-section, and between its two parallel legs directed towards the injection pump there is mounted a bearing pin for the bearing lever. It is a particularly advantageous feature that the two legs contain a guide groove each for the guides protruding on the sides of the regulator member, which feature results in a simple and low-friction guidance of the regulator member.
  • the first control spring is preferably a leaf spring, and between the two aforesaid legs of the force-transmitting lever, there is provided a fixed abutment for the leaf spring; furthermore, the said fixed abutment for the leaf spring preferably comprises a recess in each one of the two legs; the leaf spring has two laterally projecting parts at one end which engage these recesses, and the leaf spring is supported at its other end by the guide pins of the regulator member, and the adjusting screw associated therewith is secured in its position by means of a screw connection in the cross-piece of the U or H-section of the force-transmitting lever intermediate both ends of the leaf spring.
  • the arrangement of the first control spring serving as a no-load control spring, and of the adjusting screw associated therewith and with the forcetransmitting lever offers the advantage of having the influence of the first control spring upon the adjusting range of the second control spring eliminated.
  • An especially effective and space-saving embodiment is obtained by arranging at the force-transmitting lever an additional no-load spring, besides the two abovementioned control springs, which no-load spring is at least effective on part of the first portion of the displacement of the regulator member, and whose range of action is adjustable by means of an adjusting screw which is screwed into the force-transmitting lever and is secured in its position; furthermore, similar to the first control spring acting as a no-load control spring, the additional no-load spring is also designed as a leaf spring, which acts upon the regulator member by way of the first control spring; and still further, in addition a bi-metal spring is supported on the force-transmitting lever and acts upon the regulator member by way of the control spring.
  • the no-load regulating range and the idling of the motor during warm-up can be adjusted by means of the additional no-load spring and the bimetal spring in a particularly simple manner without disturbing other regulating functions.
  • FIG. 1 represents a longitudinal sectional view of the embodiment taken in a plane along line II in FIG. 2;
  • FIG. 2 is a cross-sectional view of the same embodiment taken along line IIll in FIG. 1;
  • FIG. 3 is a longitudinal sectional view taken along line III-III in FIG. 2.
  • the adaptor sleeve 15 is supported at its one end on a cylindrical stub 17 of the drive shaft 10, while its opposite end, away from the drive shaft, is fitted with laterally protruding guide pins 18, which are guided each in guide grooves 19 of a force-transmitting lever 21 (see also FIG. 3).
  • the force-transmitting lever 21 is a two-armed lever, which is pivotally secured against a pivot pin 38 fixed in the governor housing 37 and whose non-operational position as illustrated is determined by an abutment 39 fixed in the housing, the latter abutment being formed by the front end of a stop screw 41 which is screwed self-locking in the governor housing 37.
  • the force-transmitting lever 21 is of essentially U- or H-shaped cross-section, and its two legs 22 directed towards the injection pump contain the guide grooves 19 for the guide pins 18 of adaptor sleeve 15.
  • An adjusting element 23 is screwed into the cross-piece 25 of the force-transmitting lever 21 at the same level as the axis of the drive shaft 10 and the adaptor sleeve 15, and is secured in position by means of a nut 24.
  • the adjusting element 23 features an end plane 26, against which a convex surface 27 of the adaptor sleeve 15 abuts after having traversed a first part a of its path of travel.
  • first control spring 28 which is designed as a leaf spring and which has its one end 29 supported on the force-transmitting lever 21, and the other end 31 of which exerts pressure on the guide pin 18 of the adaptor sleeve 15.
  • the first end 29 of the leaf spring 28 has two laterally projecting parts 32, which are inserted into recesses 33 of the two legs 22 of the force-transmitting lever 21. These recesses 33 form a fixed abutment for the leaf spring 28.
  • a bias exerted upon the adaptor sleeve 15 is produced by an adjusting screw 34 which is screwed into the crosspiece 25 of the force-transmitting lever 21 intermediate the two ends 29 and 31 of leaf spring 28, and which is secured in its setting by means of a nut 35.
  • the force-transmitting lever 21 can be swivelled counterclockwise around the pivot pin 38. This swivelling motion takes place whenever the force originating from the centrifugal fly weights 12 and transmitted by way of the adaptor sleeve 15 and the adjusting element 23 to the force-transmitting lever is larger than the resetting force emanating from a second control spring 42.
  • This second control spring 42 is a tension spring which is arranged essentially perpendicular to the axis of the regulator member 15 in the governor and which is engaged at two abutments 43 and 44, of which the abutment 43 is located on an adjustable bearing lever 45 which serves for adjustment to the maximum rpm and which is connected with the force-transmitting lever 21 by means of a bearing pin 46 extending through the two legs 22 of the said lever 21.
  • the bearing lever 45 is designed in the form of an angle lever and its illustrated position is determined by means of an adjusting screw 47 which serves to vary the bias of the second control spring 42. This bias determines in a known manner the maximum rpm to be regulated or limited by the governor.
  • the second abutment 44 of the control spring 42 is machined in the form of a helicoidal groove 48 of semicircular profile into a bearing bolt 49 which is arranged in the governor housing 37 in a position parallel to the axis of the regulator member 15, as well as parallel to the stop screw 41 and at least approximately parallel to the adjusting screws 34, and 47 and to the adjusting element 23.
  • a rotation of this bearing bolt 49 the proportional range of the governor may be adjusted, since by rotation of the bearing bolt 49, the point of suspension, i.e., the location of the second abutment 44, of the second control spring 42 is shifted horizontally in such a manner that the active direction of the control spring 42 is changed.
  • a pressure screw 51 is screwed into the governor housing 37 in a known manner, slightly eccentrically of the central axis of bearing bolt 49 in the vicinity of one of the bearings of the said bolt 49 (see FIG. 3).
  • the linkage between the adaptor sleeve and the intermediate lever 53 is formed by a ball joint 57 (FIG. 1) consisting of a ball pin 58 and a bore 59 in a bearing arm 61 of the adaptor sleeve 15.
  • the intermediate lever 53 is in the form of a U-shaped stirrup which is pivotally mounted in the governor housing 37 by means of two ball pivots 62 (see FIG. 2 for this detail) and which is linked by means of a pin 63 with the connecting linkage 54.
  • the cam lever 54 is provided with a guide slot 64 (FIG. 3) which is engaged by a guide pin 65 of a steering lever 66 which pin is fixedly connected to a shaft 67 supported in governor housing 37.
  • An operating lever 68 (FIG.
  • lever 68 which carries at one end, outside the governor housing 37, the operating lever 68, is provided at its other end with a stop lever 71 for limiting the pivoting angle of the operating lever and thereby also that of the steering lever 66 in conjunction with known stop means (not illustrated). Both levers 68 and 71 may, of course, also be arranged on the same side of the governor.
  • an additional no-load spring 73 is engaged at the force-transmitting lever 21 in addition to the first control spring 28 serving as no-load control spring (see F IG. 1 for this detail).
  • This additional noload spring 73 is provided with a fixed spring seat in the form of a pin 74 which is mounted in the two legs 22 of the force-transmitting lever 21, and its active path b is adjustable by means of an adjusting screw 75 screw-fitted into the force-transmitting lever 21.
  • This adjusting screw 75 is, for instance, secured in its setting by means of a securing fluid.
  • the additional no-load spring 73 is provided with an angular bend 76 at one end which, after the no-load control spring 28 has travelled through path b, engages with the latter spring and assists the action of the latter on the adaptor sleeve 15.
  • a bi-metal spring 77 secured to the forcetransmitting lever 21, which spring 77 changes its position, in case of a cold engine, in such a way as to additionally act upon the regulator member 15 by way of the first control spring 28, which action results in an increased idling speed, as is required for the smooth running of a cold engine.
  • Both additionallly provided springs 73 and 77 may, ofcourse, be omitted in the case of simple regulating conditions.
  • the governor housing 37 is closed by means of a cover 78 on the frontal face thereof away from the injection pump, which cover allows, after its removal, access to all essentially horizontally disposed adjusting elements of the governor.
  • These adjusting elements are, to summarize them, the bearing bolt 49 for adjusting the proportional range of the governor, the stop screw 41 for the adjustment of the non-operational position of the force-transmitting lever 21, the adjusting screw 47 for changing the bias of the control spring 42, the adjusting screw 34 for changing the bias of the noload control spring 73, and the adjusting element 23 for the adjustment of the first partial travel a of the path of the adaptor sleeve 15, which travel a is normally identical with the idling stroke of the adaptor sleeve 15.
  • the governor operates as follows:
  • the rpm rises further and the centrifugal fly weights l2 swing outwardly, under the influence of the centrifugal forces, from their position as shown in the drawing.
  • the centrifugal fly weights 12 thereby transmit the adjusting forces with their arms 13 via the thrust collar 14 and the thrust bearing 16 to the adaptor sleeve 15, which is displaced against the force of the no-load control spring 28 until it abuts with its front face 27 at the end plane 26 of the adjusting element 23, which is screw-fitted into the force-transmitting lever 21.
  • This displacement of the adaptor sleeve 15 by the partial travel path a causes the bearing arm 61 with the ball joint 57 to be displaced by the same length of travel, and the control rod 56 is shifted by means of the linkage members 53, 54 and 55 from the starting position into the full load position.
  • the governor remains in this position as the rpm increases further until the final rpm is reached, which is predetermined by the bias of the second control spring 42 serving as main control spring. If this final rpm is exceeded in the case of the engine operating under partial load, the force transmitting lever 21 lifts off its stop 39 due to the increasing force at the adaptor sleeve 15, and the latter travels further beyond the partial distance a.
  • the adaptor sleeve 15 thereby moves the linkage members 53, 54, 55 and the control rod 56 into a position in which the fuel quantity of the injection pump is decreased until it corresponds with the power output of the motor and until the rpm is maintained within the proportional range.
  • the linkage members 53, 54 and 55 are free from resetting forces in all operating conditions.
  • the centrifugal rpm-regulating governor according to this invention is particularly suited for an automated setting. But even without such automated setting, the centrifugal governor according to the invention offers the advantage that all adjusting elements are accessible from one end only, and that they can be adjusted independently of each other, i.e., without influencing the function of other adjusting elements.
  • a further advantage resides in the fact that the noload control spring 28, the additional no-load spring 73, as well as the bi-rnetal spring 77 with their associated adjusting screws 34 and 75 are supported at the force-transmitting lever 21, whereby these springs are fixedly clamped, upon abutment of the front face 27 of the adaptor sleeve at the supporting lever 21, or at its adjusting element 23, so that they no longer have any influence on the regulation of the final rpm.
  • a further advantage to be noted is that the spacings of the adjusting elements 23, 34, 41, 47, 49 and 75 do not change during the various adjusting procedures, but remain constant, which fact facilitates a rapid and optionally an automated setting of the governor, as, for this purpose, a multiple-adjusting tool having adjusting means arranged in parallel can be applied from the front end of the regulator.
  • a centrifugal governor for controlling the rpm of an injection type internal combustion engine having a fuel injection pump, which governor has a housing and a regulator member being displaceable as a function of the rpm, and the regulating movements of which member are transmitted, by means of a two-armed cam lever having lever arms which are adjustable dependent upon the position given an externally turnable operating lever, to fuel delivery control means associated with said fuel injection pump, wherein said fuel delivery control means, upon completing a first part of its movement against the force of a first control spring, acts on a force-transmitting lever which is biassed by at least one second control spring, and said force-transmitting lever bears an adjusting screw for setting said first control spring to a low rpm, and is adapted for swivelling about an axis which is stationary in said housing, and wherein the neutral position of said force-transmitting lever is determined by a stop fixed in said housing, the improvement comprising a. a bearing lever adjustable for setting a maximum rpm and bearing a
  • bearing lever, second adjusting screw and adjusting element being in engagement with said forcetransmitting lever.
  • bearing lever is an angle lever having a pivot axis stationary relative to said force-transmitting lever.
  • said second control spring is a tension spring which is disposed at least approximately in parallel with said force-transmitting lever.
  • said force-transmitting lever is of U- or l-l-type cross sectional configuration and has two parallel legs facing toward said injection pump.
  • each of said legs is provided with a guiding slot
  • said regulator member is provided with a pair of guide-pins being inserted each in one of said guiding slots.
  • said first control spring is a leaf spring
  • said adjusting screw for said first control spring is screw-connected to and secured in position at said force-transmitting lever in the cross part thereof intermediate said two legs and engages said leaf spring intermediate the ends thereof.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
US00362302A 1972-05-20 1973-05-21 Centrifugal governor for controlling the rpm of injection type internal combustion engines Expired - Lifetime US3830211A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2224755A DE2224755C3 (de) 1972-05-20 1972-05-20 Fliehkraftdrehzahlregler für Einspritzbrennkraftmaschinen

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US3830211A true US3830211A (en) 1974-08-20

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US00362302A Expired - Lifetime US3830211A (en) 1972-05-20 1973-05-21 Centrifugal governor for controlling the rpm of injection type internal combustion engines

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US (1) US3830211A (ja)
JP (1) JPS561461B2 (ja)
AT (1) AT323469B (ja)
BR (1) BR7303237D0 (ja)
CS (1) CS161817B2 (ja)
DE (1) DE2224755C3 (ja)
FR (1) FR2186068A5 (ja)
GB (1) GB1405368A (ja)
IT (1) IT973293B (ja)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3884206A (en) * 1973-02-20 1975-05-20 Bosch Gmbh Robert Centrifugal rpm regulator for internal combustion engines
US3970066A (en) * 1973-10-03 1976-07-20 Robert Bosch G.M.B.H. RPM regulator for fuel injection pumps
US3973542A (en) * 1973-03-06 1976-08-10 C.A.V. Limited Liquid fuel injection pumping apparatus
US4085724A (en) * 1975-06-12 1978-04-25 Robert Bosch Gmbh Fuel regulator for internal combustion engines with injection system
US4340020A (en) * 1978-11-11 1982-07-20 Lucas Industries Limited Governor mechanism
US4479474A (en) * 1981-08-06 1984-10-30 Robert Bosch Gmbh Rpm Governor for fuel-injected internal combustion engines, in particular a final idling rpm governor of an injection pump for diesel vehicle engines
US5752483A (en) * 1995-09-01 1998-05-19 Lucas Industries, Plc Governor arrangement

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3970064A (en) * 1974-01-23 1976-07-20 Robert Bosch G.M.B.H. RPM regulator for fuel injection pumps
DE2644994A1 (de) * 1976-10-06 1978-04-13 Bosch Gmbh Robert Drehzahlregler fuer einspritzbrennkraftmaschinen
DE2855889A1 (de) * 1978-12-23 1980-07-10 Bosch Gmbh Robert Fliehkraftdrehzahlregler fuer einspritzbrennkraftmaschinen, insbesondere leerlauf-enddrehzahlregler fuer fahrzeugdieselmotoren
DE2900198A1 (de) * 1979-01-04 1980-07-17 Bosch Gmbh Robert Fliehkraftdrehzahlregler fuer einspritzbrennkraftmaschinen, insbesondere leerlauf-enddrehzahlregler fuer fahrzeug-dieselmotoren
JPS58150681A (ja) * 1982-03-02 1983-09-07 ドリ−ム自動ドア工業株式会社 扉の開閉装置
JPS58183883U (ja) * 1982-06-02 1983-12-07 東欧電機株式会社 扉
GB2130241B (en) * 1982-09-24 1986-01-15 Nippon Steel Corp Method for producing a grain-oriented electrical steel sheet having a high magnetic flux density
JPS5960275U (ja) * 1982-10-14 1984-04-19 寺岡オ−ト・ドア販売株式会社 扉開閉機構
JPS6120767U (ja) * 1984-07-10 1986-02-06 ワイケイケイ株式会社 扉の水平保持装置
JPS6120878U (ja) * 1984-07-10 1986-02-06 ワイケイケイ株式会社 扉の水平保持装置
JPS6125486U (ja) * 1984-07-18 1986-02-15 株式会社ナブコ 開き戸装置付引き戸ドア
DE3529421C2 (de) * 1985-08-16 1994-12-08 Bosch Gmbh Robert Fliehkraftdrehzahlregler für Brennkraftmaschinen
DE3932414A1 (de) * 1989-09-28 1991-04-11 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2241096A (en) * 1937-12-24 1941-05-06 Pierce Governor Company Wide range governor for diesel engines
US3577968A (en) * 1968-10-17 1971-05-11 Bosch Gmbh Robert Centrifugal r.p.m. regulator for internal combustion engines
US3620199A (en) * 1969-01-08 1971-11-16 Bosch Gmbh Robert Contrifugal governor for the rpm control of internal combustion engines
US3714935A (en) * 1971-09-15 1973-02-06 Allis Chalmers Multiple plunger fuel injection pump
US3759236A (en) * 1970-10-03 1973-09-18 Bosch Gmbh Robert Centrifugal governor for regulating the rpm of internal combustion engines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2241096A (en) * 1937-12-24 1941-05-06 Pierce Governor Company Wide range governor for diesel engines
US3577968A (en) * 1968-10-17 1971-05-11 Bosch Gmbh Robert Centrifugal r.p.m. regulator for internal combustion engines
US3620199A (en) * 1969-01-08 1971-11-16 Bosch Gmbh Robert Contrifugal governor for the rpm control of internal combustion engines
US3759236A (en) * 1970-10-03 1973-09-18 Bosch Gmbh Robert Centrifugal governor for regulating the rpm of internal combustion engines
US3714935A (en) * 1971-09-15 1973-02-06 Allis Chalmers Multiple plunger fuel injection pump

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3884206A (en) * 1973-02-20 1975-05-20 Bosch Gmbh Robert Centrifugal rpm regulator for internal combustion engines
US3973542A (en) * 1973-03-06 1976-08-10 C.A.V. Limited Liquid fuel injection pumping apparatus
US3970066A (en) * 1973-10-03 1976-07-20 Robert Bosch G.M.B.H. RPM regulator for fuel injection pumps
US4085724A (en) * 1975-06-12 1978-04-25 Robert Bosch Gmbh Fuel regulator for internal combustion engines with injection system
US4340020A (en) * 1978-11-11 1982-07-20 Lucas Industries Limited Governor mechanism
US4479474A (en) * 1981-08-06 1984-10-30 Robert Bosch Gmbh Rpm Governor for fuel-injected internal combustion engines, in particular a final idling rpm governor of an injection pump for diesel vehicle engines
US5752483A (en) * 1995-09-01 1998-05-19 Lucas Industries, Plc Governor arrangement

Also Published As

Publication number Publication date
CS161817B2 (ja) 1975-06-10
IT973293B (it) 1974-06-10
DE2224755A1 (de) 1974-01-17
DE2224755B2 (de) 1978-04-27
GB1405368A (en) 1975-09-10
JPS4943030A (ja) 1974-04-23
DE2224755C3 (de) 1978-12-07
FR2186068A5 (ja) 1974-01-04
AT323469B (de) 1975-07-10
JPS561461B2 (ja) 1981-01-13
BR7303237D0 (pt) 1974-06-27

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